Shuttle boxing method and apparatus

ABSTRACT

There is disclosed a shuttle boxing method and apparatus whereby loom shuttles, upon completion of their traverse of the lay beam, are rapidly and smoothly decelerated without deleterious rebound. The deceleration method and apparatus of the invention serve to employ the kinetic energy of the flying shuttle in overcoming the inertia of a flywheel at rest. In the picking or firing cycle embodiment of the invention the energy of the spinning flywheel is imparted to the boxed shuttle.

[ Feb. 26, 1974 SHUTTLE BOXING METHOD AND 2,787,290 Rapp et al. 1,966,704 7/1934 Bell et al....... 3,670,775 6/1972 APPARATUS [75] Inventor: William J. Stephens, Bedford, Mass.

[73] Assignee: Noxxe, Inc., Bedford, Mass. Primary Examinerjames Kee Chi Attorney, Agent, or FirmBarry R. Blaker [22] Filed: Feb. 28, 1972 [21] Appl. N01: 229,697

[57] ABSTRACT There is disclosed a shuttle boxing method and appa- 52 us. 139/185, 139/142, 139/162 Paws whereby 100m Shuttles, upon Completion of their 511 Int. Cl.. 00341 49/54, D03d 49/24, 1303a 49/38 traverse of the lay beam, are rapidly and smoothly decelerated without deleterious rebound. The decelera- [58] Field of Search.................... 139/185187, 142,

tion method and apparatus of the invention serve to employ the kinetic energy of the flying shuttle in over- 56] References Cited coming the inertia of a flywheel at rest. In the picking UNITED STATES PATENTS or firing cycle embodiment of the invention the energy of the spinning flywheel is imparted to the boxed shuttle.

139/142 10 Claims, 8 Drawing Figures I "Ht H "H lnn ay "tn a Ii 6 WW 3 M fy PSV 400 675 999 111 3 00 604 665 477 28 332 PATENTED FEB26 I974 SHEET 1 BF 5 FIG.

PATENTED FEB 2 61974 SHEET 5 0F 5 FIG. 5

SH BOXING METHOD AND APPARATUS FIELD OF THE INVENTION The present invention relates broadly to textile looms and operations thereof. More specifically, the method and apparatus disclosed and claimed herein relate to operations conventionally known in the art as shuttle boxing and picking.

With the ever increasing demands placed upon textile manufacturers to increase loom speed and thereby increase loom output, it has become commonplace practice to impose heavy operating loads on textile looms. Obviously, loom speeds cannot be increased beyond those limits which are consistent with smooth mill operations and textile quality.

One of the major problems confronted in the textile loom art throughout its history, and particularly when high production rate loads are imposed upon a loom, resides in the phenomenon of shuttle rebound. It is quite common in present day loom operations to pick or fire the shuttle across the race board of the'loom at velocities substantially in excess of thirty miles per hour. At the end of each pick, however, it is allimportant that the shuttle be stopped without bounce or rebound from or within the shuttle box. Unfortunately, however, when a rapidly moving shuttle engages shuttle boxes of conventional designs of the prior art, rebound thereof often occurs. The conventional shuttle box designs generally include friction means adapted to bear against the shuttle upon entry thereof into the box, thereby decelerating and halting the shuttle. Such binder mechanisms thus depend upon the conversion of the kinetic energy of the shuttle into heat. Designs of this type are exemplified, for instance, in the disclosures of U.S. Pat. Nos. 2,874,727; 3,012,586 and 3,593,755. Other known shuttle boxing protection devices include mechanical dogs, pawls or the like which are adapted to engage the shuttle upon entry thereof into the box and to release the shuttle prior to its subsequent pick. Each of the shuttle box mechanisms described above have associated therewith certain serious deficiencies. Above all, the most serious of said deficiencies resides in the fact that none appear to have totally resolved the problem of shuttle rebound. The mechanical pawls and friction inducing means of the prior art shuttle boxes further tend to wear rather rapidly, thus requiring a considerable amount of maintenance. Even when operating properly, however, which proper operations also depend upon tedious and time consuming fine tuning of the mechanism, the normal dimensional allowances of such devices generally allow at least some deleterious rebound of the shuttle. Said rebounding, even if ofa minor nature, can often result in what is termed in the art as a slack pick or loose fill" which is visually detectable in the completed textile as a streak across the warp thereof. More seriously, even slight rebound of the shuttle tends to be a progressive phenomenon which results in increasing spacing between the shuttle and the picker stick in subsequent picks. Occasionally, said spacing becomes so great as to ultimately cause the velocity of the picked shuttle to fall below that necessary to traverse the race board and enter fully into the shuttle box. A similar situation can also arise when the shuttle boxing mechanism fails to engage or bind the shuttle within the box. In either case, the result of shuttle rebound of this magnitude is often a catastrophic smash-out wherein the shuttle is trapped in the warp shed during the repositioning of the harnesses. Such smash-outs almost invariably destroy the warp yarns and, in any case, require complete shutdown and rethreading of the loom. Thus, the deleterious phenomenon of shuttle rebound has been adjudged to contribute as much as one-third of the total down time of commercial loom operations.

Yet another problem involved in operations of conventional shuttle box binding and picking apparatus resides in the relatively large contribution made by such apparatus to the overall noise levels produced by a loom. Thus, the noise levels attained in the weaving rooms of textile mills are often sufficiently great as to be adjudged hazardous to the hearing of the workers.

In accordance with the present invention, however, the above problems have been substantially ameliorated.

OBJECTS OF THE INVENTION It is a principal object of the invention to provide a novel method for boxing shuttles in textile loom operations.

It is another object of the invention to provide novel apparatus for the boxing of loom shuttles wherein shuttle rebound is substantially completely eliminated.

Another object of the invention is to provide a novel method for both boxing and picking loom shuttles.

It is still another object of the invention to provide shuttle boxing and picking apparatus for the reception and firing of loom shuttles which apparatus substantially reduces the overall noise generated by a loom equipped therewith.

It is another object of the invention to provide novel shuttle 'boxing and picking apparatus which apparatus substantially avoids the necessity for fine tuning thereof and which apparatus is relatively insensitive to minor deviations in loom operations.

It is a further object of the invention to provide novel shuttle boxing and picking apparatus for the reception and firing of shuttles wherein at least a portion of the energy given up by the shuttle upon reception thereof is stored and returned thereto upon firing.

Other objects and advantages of the present invention will in part be obvious and will in part appear hereinafter.

GENERAL DESCRIPTION OF THE INVENTION The loom shuttle receiving and deceleration method of the invention comprises the transfer of the kinetic energy of a moving shuttle to a flywheel. The apparatus by which said method is carried out includes a shuttle target which, through a suitable mechanical linkage, translates the linear displacement imparted thereto by the impacting shuttle to an angular displacement output. The angular displacement output is transmitted to a resting flywheel by means of a suitable clutch device interposed between the linkage and the flywheel. Firing or picking of the shuttle brought to rest by the method and apparatus described above is accomplished by transferring the energy and translating the rotational displacement of the spinning flywheel, again through suitable clutch means and said mechanical linkage to a linear output displacement of the shuttle target, thereby firing the shuttle in its reverse course across the race board of the loom. Accordingly, at least a portion of the energy imparted to the flywheel by the shuttle boxing cycle is stored and returned to the shuttle in the picking cycle. To make up energy losses suffered in internal friction through the linkage and spinning of the flywheel the energy input to the flywheel is augmented by fixed attachment thereof to a prime mover adapted to rotate in either direction of rotation. The direction of rotation of said prime mover is dictated by the direction of initial movement of the flywheel in the previous shuttle boxing cycle.

THE DRAWINGS A better understanding of the present invention can be had by reference to the drawings forming part hereof, wherein:

FIG. 1 is a schematic, diagrammatic, partly sectional perspective view of a portion of a conventional flyshuttle loom equipped with the shuttle boxing and picking apparatus of the invention;

FIG. 2 is a longitudinal section of clutch apparatus suitable for use in the apparatus of FIG. 1 and shown in the disengaged position;

FIG. 3 is a sectional plan view of the clutch mechanism of FIG. 2 in the engaged position, taken through section line 1-1' thereof;

FIG. 4 is a perspective, partly sectional view of the principal clutch engagement and disengagement actuating members of the clutch mechanism of FIGS. 2 and 3; and

FIGS. 5 through 8 are schematic, diagrammatic side views of the mechanical linkage mechanism employed in FIG. 1 wherein the relative positions of the-various linkage elements thereof are shown at several stages of operations in the shuttle receiving and firing cycles of the apparatus of the invention.

DETAILED DESCRIPTION OF THE INVENTION Referring now generally to FIGS. 1 through 8, wherein like reference numerals refer to like elements, and particularly to FIG. I, lay beam 50 defines generally a race board 51 along which shuttle 55 traverses the warp shed (not shown) and shuttle box 52 wherein the shuttle is received, arrested, allowed to dwell for a time sufficient to provide suitable changeover of the harnesses (not shown) and fired in its return pick. The shuttle boxing mechanism of the invention comprises shuttle target 11, mechanical linkage 20, clutch 20d) and flywheel 70. Said mechanical linkage 20 is adapted to (A) provide for substantially linear and parallel displacement of target 11 with respect to the shuttle box bed 54, while (B) translating said linear displacement into an angular displacement output at a convenient point removed from the shuttle box 52. In the particular linkage 20 shown (referring to FIGS. 1, 5 and 7), linkage element 1 is pivotally affixed at its upper end to target 11 and is pivotally affixed at its midpoint to the lower end of linkage element 2. The lower end of linkage element 1 comprises a common and mutually pivotal attach point for both the upper end of linkage element 3 and the right hand end of linkage element 5. The upper end of linkage element 2 is pivotally affixed to a stationary base which may reside in slot 56 of lay beam 50. Similarly, the upper ends of linkage elements 6 and 7 are affixed in pivotal manner to a stationary base while the lower ends of said elements 6 and 7 are pivotally affixed to linkage element 5 at the midpoint and left hand end thereof, respectively. Finally, the lower end of linkage element 3 is pivotally attached to the upper end of terminal linkage element 4. The lower end of said linkage element 4 is pivotally mounted in coaxial relationship with the center of flywheel 70. Clutch 200 is adapted to transfer angular displacement of terminal linkage 4 to the flywheel. One such suitable clutch will be discussed in more detail hereinbelow.

In a shuttle receiving and decelerating (or boxing) cycle, referring especially to FIGS. 1, 5 and 7, shuttle 55 strikes target 11, thereby linearly displacing said target 11 over the bed 54 of shuttle box 52 and towards the end 57 of lay beam 50. Said substantially linear displacement actuates linkage mechanism 20 causing either a clockwise or counterclockwise angular displacement of terminal linkage element 4. In turn, the initiation of the angular displacement of element 4 either causes or finds clutch 200 in engagement with resting flywheel 70, thereby overcoming the flywheels inertia and initiating and accelerating the rotation thereof while concomitantly transferring the kinetic energy of the shuttle 55 to the flywheel 70. The end of the shuttle decelerating cycle (FIGS. 6 or 8) is signalled with the knee formed between articulated linkage elements 3 and 4 has been straightened so as to position said elements coaxially with respect to one another and the target 11 has been moved to its rearmost position. At this point, clutch 200 disengages element 4 from flywheel 70, thereby allowing flywheel to freewheel. The direction of rotation of flywheel 70 will be determined by the position of the knee formed between articulated linkage elements 3 and 4 at the beginning of the cycle. As is clearly shown in FIGS. 4 and 5, when said knee is positioned to the left at the beginning of the shuttle receiving cycle, the flywheel will spin in clockwise direction. However, referring now to FIGS. 7 and 8, when the knee formed between articulated elements 3 and 4 is positioned to the right upon initiation of the shuttle receiving cycle, the resulting rotation of the flywheel will be in a counterclockwise direction.

Having arrested the motion of the shuttle in a smooth and essentially reboundless manner, the resetting of the shuttle decelerating apparatus of the invention in preparation for the subsequent shuttle receiving cycle is accomplished merely by bringing the spinning flywheel 70 to rest and moving target 11 to its forward position. The flywheel 70 may be brought to a halt by any suitable braking means (not shown) actuated in proper time sequence with respect to the weaving cycle of the loom. Such braking, for instance, may be actuated upon firing of the shuttle from the shuttle box. Similarly, the target 11 can be brought to its forward position by means of a separate picker stick (not shown) positioned therebehind.

The decelerating forces applied to the shuttle in carrying out the shuttle boxing method of the present invention are such as to insure the arresting of the shuttle with little or no danger of rebound. While there is no intent to be bound by this explanation, it is thought that the beneficially rebound-free nature of the present shuttle boxing method and apparatus is due to the inherent nature of the energy transfer involved in overcoming the inertia of a resting rotatable mass, i.e., the flywheel 70 inertia reflected to the shuttle 55 at the time of initial engagement with target 11 is essentially zero and, as the shuttle penetrates into the boxing apparatus, this reflected inertia increases due to the chaning mechanical advantages associated with the instantaneous position of the linkage 20 until, when the shuttle is deep into the boxing apparatus, this reflected inertia tends towards infinity. Thus, there is presented a higher and higher inertial load for the penetrating shuttle to accelerate. in this context, it can be demonstrated that the characteristic curve of shuttle deceleration as a function of its position in the boxing apparatus results in a deceleration peak occurring prior to the end of its travel into the box and a decline to zero deceleration at its deepest travel into the box. Therefore, the linkage is inherently relieved of forces at the end point of the boxing cycle, absenting any tendency thereof to rebound the shuttle.

Where the loom to be equipped with the shuttle receiving apparatus of the invention is of the Sulzer type, in other words where the shuttle or dart is fired across the lay beam in one direction only, picked up and returned to the firing side of the warp shed, only one of the shuttle receiving and decelerating devices of the invention is required. in most instances, however, where conventional fly-shuttle looms are to be equipped, it will be obvious that the shuttle boxes on both sides of the lay beam be equipped with the shuttle receiving and decelerating devices described and claimed herein. Further with respect to conventional fly-shuttle looms, after having decelerated and arrested the shuttle by the apparatus disclosed in detail hereinbefore, said shuttle may be fired by conventional picker stick means. A much preferred embodiment of the invention, however, eliminates the need for such added picker stick means and serves further to converse and re-use a substantial portion of the energy originally imparted to the flywheel in the deceleration of the shuttle during the receiving cycle.

in achieving the picking or firing cycle, in addition to the receiving and decelerating apparatus already disclosed, there is also provided a prime mover 300 which is adapted for rotation of its shaft 301 in either direction upon mechanical initiation of rotation thereof. A principal example of a prime mover possessed of this attribute is a single phase electric motor whose conventional electrical starting apparatus has been disabled. Shaft 301 is fixed to flywheel 7t) and, indeed, desirably forms the common shaft for mounting of the flywheel and the freely rotatable spindle 605 of clutch Ztltl (FIGS. 2, 3 and 4). As will be recalled with respect to the discussion concerning the characteristics of the shuttle receiving cycle at termination thereof, target 11 is positioned at its rearmost position, clutch 200 is disengaged and flywheel 70 is freewheeling. Strictly speaking, however, when the shuttle firing embodiment of the invention is employed, said freewheeling does not occur. Rather, the initial motion of flywheel 70 in the shuttle receiving and decelerating cycle acts through shaft 301 to actuate prime mover 300. Thus,

in this case, the termination of the shuttle receiving and r decelerating cycle is signalled by the rearmost position of target 1 ll, disengagement of clutch 200 and continuing acceleration of flywheel 70 by means of the continuing action of prime mover 300. Prior to initiation of the .shuttle firing cycle, flywheel 7tlwill generally attain the slip-speed of the prime mover 30ft.

rate timing of the initiation of shuttle firing sequence is available. Thus, the clutch engagement signal may be derived from sensing and responding to the position of lay sword 700. For example, clutch 200 engagement may be obtained through a motion reversing means whereby trigger 650 is actuated by the rearward motion of lay sword 700. Other portions of the loom may be employed, however, such as the dobby head, harness cams, crankshaft or any other loom part from which the relative positions of the harnesses and lay beam can be accurately and repetitively determined. In any case, upon engagement of clutch 200, the spinning flywheel imparts its energy to shuttle 55 through the linkage mechanism 20 and target 11. Target ll, propelled forwardly along shuttle box bed 52, thereby accelerates shuttle 55 to its pick speed. The finish of the shuttle firing cycle finds target 11 in its forwardrnost position and the knee formed between linkage elements 3 and 4 fully reconstituted. Accordingly, initiation of the shuttle firing cycle from the position shown in FIG. 5, with clockwise spinning of flywheel 7t), will result in the finish linkage 20 position shown in FIG. 7. Conversely, where the shuttle firing sequence is initiated from the linkage 20 conformation shown in F lG. 8, wherein the flywheel 70 is spinning in counterclockwise rotation, the finish position will be that shown in FIG. 5. The attainment of the linkage 20 positions shown in FIGS. 5 and 7 brings linkage element 1 to its maximum angular displacement from the vertical. In turn, this linkage geometry through transfer of forces through the linkage 2t) and clutch 20th smoothly and rapidly decelerates flywheel '70 and prime mover 300 to a complete halt. At the endpoint in the shuttle firing sequence, therefore, the shuttle boxing and firing mechanism of the invention bears the conformation shown in FIGS. 5 and 7 and is prepared to receive the shuttle of the subsequent pick.

Generally speaking, the design and material considerations pertinent in the shuttle receiving and firing mechanism of the invention are within the ambit of those skilled in the art. It is obvious, for instance, that the linkage elements be constructed so as to withstand the operating stresses imposed thereupon. In this context, it is to be noted that the particular preferred em bodiment of the linkage 20 described in detail hereinabove can be generally described as two lsosceles type linkages connected back to back. One of said linkages is defined by the combination of linkage elements 5, 6 and '7 while the other is defined by the combination of linkage elements 1 and 2. The resulting overall linkage operates with marked freedom from torsional stresses, the bulk of the operating stresses being purely compressive or tensional in nature. Other suitable linkage assemblies are known, however, wherein a linear motion input is translatable into an angular motion output and, vice versa. For instance, another suitable linkage 20 design comprises a vertical race depending from the bottom of the lay beam. A sliding member rides up and down on said vertical race and additionally comprises (1) a connecting linkage element attached in pivotal manner to the shuttle target, and (2) a two-element articulated toggle assembly, one of which toggle elements is affixed in pivotal manner to the sliding member and the other of which toggle elements is rotatably affixed to the flywheel shaft. In this arrangement, therefore, this last toggle element comprises the angular displacement member of the overall linkage. Said type of linkage has the advantage of fewer moving parts than the linkage described in detail hereinbefore. However, the sliding member thereof can impart substantial sliding friction into the overall system. With respect to such frictional considerations, moreover, it is obviously desirable that the linkage elements be provided with suitable bearings at their respective articulations so as to minimize frictional energy losses through the system.

The flywheel 70 size, weight and design is subject to considerable variation and is dependent upon the mass and velocity of the shuttle at the impact point thereof against target 11, frictional losses through the linkage 20, the energy required to drive the clutch mechanism 200 and the like. Accordingly, bearing the above in mind, the size, mass and specific design of the required flywheel or rotatable mass can be determined for any given loom situation. The primary goal to be achieved, of course, is to provide a flywheel of sufficient inertial characteristics as to smoothly decelerate the shuttle to zero velocity. When the apparatus of the invention includes the shuttle firing embodiment, i.e., the prime mover 300, the contribution said prime mover may make upon start-up thereof to the acceleration of the flywheel prior to clutch disengagement and/or the contribution said prime mover may make to the overall flywheel function should also be taken into account in determining suitable flywheel mass and size.

A suitable clutch mechanism for use in the apparatus of the invention is depicted in detail in FIGS. 2 through 5 forming part hereof. Shaft 301 which, as mentioned before, may desirably be the shaft of prime mover 300, traverses housing 204, bearing 610, flywheel 70, spin dle 605 and bearing 612. Terminal linkage element 4 is rigidly affixed to spindle 605 which, in turn, is mounted rotatable and slideably upon said shaft 301. Spindle 605 comprises a generally l-I-shaped member to which triangular toggle arms 606 and 607 are pivotally affixed, such as by pinning thereof. Important in the operation of the toggle mechanism are elongated apertures 608 and 609 of spindle 605, which apertures allow toggle members 606 and 607 to rock in an offaxis manner when the clutch is actuated and/or engaged. Completing the toggle assembly are friction pad holders 610 and 611, each being pivotally affixed to the apex of triangular toggle arms 606 and 607 and to which pad holders there are attached friction pads 612 and 613. In the disengaged mode of the clutch (FIG. 2), said friction pads 612 and 613 ride close to but out of contact with the internal flange surface 72 of flywheel 70. In the engaged clutch mode (FIG. 3) said pads 612 and 613 are tightly bound against said internal flange surface 72, thereby effectuating the transmission of power between the spindle 605 and flywheel 70. As will be noted with respect to the engaged mode of operation, toggle members 606 and 607 rock in a slightly off-axis fashion and thus provide for the desirably greater available bearing force between pads 612 and 613 and the internal flywheel surface 72. Furthermore, said rocking motion tends to cause the clutch to self-energize, once initial actuation thereof has been achieved. Accordingly, the rocking motion of toggle members 606 and 607 is highly advantageous and contributes materially to the rapidity of clutch engagement and to the ultimate security of said engagement. Finally, depending from and integral with spindle 605 are cam roller 614 and friction stud 615, said stud 615 having affixed to the terminus thereof friction pad 616.

The clutch actuating mechanism comprises sliding block 617 having on the upper surface thereof disengage cam 618 and a double wedge vertical protuberance 619. Lower surface 610 of recess 621 also defines a cam surface adapted to receive in operative combination therewith cam stud 651 of actuating trigger 650. Finally, to housing 204 there are afflxed ring-shaped members 206 and 207 whose internal circumferential surfaces define clutch lock-in cam surfaces 208 and 210. It should be noted that said semi-circular members 206 and 207 need only to subtend an are equal to or somewhat greater than the total are traversed by terminal link member 4 in its to and fro motion about the axis formed by shaft 301.

In operation, taking now the condition wherein the shuttle is resting in the shuttle box awaiting the next pick thereof, tenninal link element 4 will be found in the vertical position (FIGS. 6 or 8). Accordingly, in this condition clutch 200 will be in the disengaged position of FIG. 2 wherein friction stud 615 of spindle 605 bears against the double wedge protuberance 619 of sliding block 617, thereby spacing said block in the raised position thereof under the influence of compression spring 622. More particularly, said raised position of the block 617 maintains cam roller 614 positioned over the apex of disengage cam 618. Upon pick-off of the firing signal from a suitable source, actuating trigger 650 is mechanically and momentarily driven into slot 621 of blcok 617, cam 651 thereby lowering said block and moving cam 618 out of engagement with cam roller 614. Next, stud 653 of trigger 650 drives into cam roller 614. This last action serves to force cam roller 614 onto either one of the lock-in cam surfaces 208 or 210 depending on the direction of rotation of flywheel 70. The cam roller 614 is thus forced forwardly by cam surface 208 or 210 and carries with it spindle 605, thereby forcing toggle members 606 and 607 and their associated friction pads 612 and 613 against the interior flange surface 72 of flywheel 70, thus completing the engagement of the clutch and effectuating the firing of the shuttle. In a preferred embodiment of the invention, wherein both the shuttle receiving and firing functions are carried out by the claimed apparatus, the clutch remains engaged subsequent to the shuttle firing cycle and in preparation for the initiation of the next shuttle receiving cycle.

In the shuttle receiving cycle the terminal link 4 will be at its furthest angular deflection from the vertical (FIGS. 5 or 7) and flywheel and prime mover 300 will be halted. Upon impact of the shuttle against the shuttle target 11, terminal link element 4 is set into motion towards the vertical position, thereby initiating rotation of flywheel 70 and prime mover 300 by transfer of the motion thereof through the engaged clutch. As terminal link 4 approaches the vertical, cam roller 614 is forced outwardly by disengage cam 618, thus withdrawing spindle 615 from its forwardmost position and disengaging the clutch. Upon said disengagement, flywheel 70 continues spinning and is even further accelerated to the slip-speed of prime mover 300 while leaving shuttle target 11 in its rearmost position and terminal linkage element 4 at substantially the vertical position, thus providing the appropriate conditions for the subsequent firing cycle.

While the clutch mechanism discussed above has been described in detail, it will be obvious that many equivalents thereof can also be employed in the practice of the invention. Accordingly, it is only necessary that the clutch mechanism employed (1) be capable of engaging and disengaging immediately upon appropriate command thereof, (2) be sufficiently sturdy as to withstand the relatively high and instantaneously applied torque loads imposed thereupon during operations and (3) be bi-directional in operation. For instance, clutches based on the well-known spring wrap principle wherein use is made of the capstan effect encountered when a coiled flat spring is wound or tightened about an arbor are also considered suitable for the practice of the invention. in this embodiment, two such devices in back-to-back relationship will achieve the necessary bi-directional function of the overall clutch mechanism.

Also, the drive shaft of the prime mover, when employed, need not be affixed directly to the hub of the flywheel. For instance, said shaft can be equipped with pinion teeth adapted for geared engagement with the exterior periphery of the flywheel, thereby establishing.

the driving relationship therewith. In this case, of course, the drive shaft of the prime mover will rotate in a direction opposite that of the flywheel. Further, the prime mover/flywheel drive interfacing can include roller chain and sprocket or other conventional means for the transfer of power between a prime mover and a rotatable body or mass.

Accordingly, while i have disclosed and described my invention in detail with respect to certain specific embodiments thereof for the purposes of illustration, it will, of course, be understood that the invention is not to be construed as limited thereby, since it is apparent that the principles herein disclosed are susceptible of numerous embodiments and permutations. Accordingly, modification may be made in the method and in the structural arrangements and in the instrumentalities described hereinabove without departing from the spirit and scope of my invention as set forth in the appended claims.

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. A cyclic shuttle boxing method for textile loom operations wherein each boxing cycle comprises:

a. bringing a shuttle to be boxed into substantially frictionless contact with a shuttle target adapted for substantially linear displacement from a forward position in a shuttle box to a rear position;

b. converting the resulting rearward, substantially linear, displacement of said shuttle target into an angular displacement at a location removed from the shuttle box;

c. communicating said angular displacement to a rotatable inertial mass at rest, thereby accelerating rotation of said inertial mass while decelerating said shuttle to a complete halt; and

(1. prior to the next boxing cycle,

i. removing said shuttle from the shuttle box;

ii. halting rotation of said inertial mass and iii. returning said shuttle target to its forward position.

2. The method of claim ll wherein, subsequent to boxing of said shuttle, picking thereof is achieved, timed to loom operations, by reestablishing communi cation of said rotating inertial mass with said shuttle target, thus transferring at least a portion of the kinetic energy of said rotating inertial mass to said shuttle target by, seriatim, converting rotational motion of said rotating inertial mass to an angular displacement and converting said angular displacement to a substantially linear forwardly directed displacement of said shuttle target to said forward position thereof, thereby picking said shuttle out of said shuttle box and efiectuating steps (d) (i) and (d) (iii).

3. The method of claim 2 wherein step (d) (ii) is achieved as said shuttle target attains said forward position.

4. The method of claim 2 wherein acceleration of said rotation of said inertial mass is augmented prior to said reestablishment of communication of said rotating inertial mass with said shuttle target.

5. The method of claim 4 wherein said augmentation of acceleration of rotation of said inertial mass is achieved by communication thereof with an electric prime mover and acceleration to the slip-speed of said prime mover is attained prior to said reestablishment of communication of said rotating inertial mass with said shuttle target.

6. Shuttle boxing apparatus for textile looms comprising:

A. a shuttle box having disposed therein a shuttle target adapted for substantially linear displacement between a forward position and a rear position by a shuttle received thereagainst;

B. linkage means adapted for translation of said substantially linear displacement of said shuttle target to an angular displacement output at a location remote from said shuttle box;

C. rotational inertial mass means adapted for discontinuous operative communication with the angular displacement output of said linkage means, said operative communication occurring during the period of displacement of said shuttle target from said forward position to said rear position and ceasing upon attainment of said rear position; and

D. means to bring said rotatable inertial mass means to a halt and means to return said shuttle target to said forward position prior to each shuttle boxing cycle.

7. The shuttle boxing apparatus of claim 6 additionally comprising:

E. prime mover means in driving relationship with said inertial mass means, said prime mover means being adapted to drive said rotatable inertial mass means only upon rotation thereof and in either direction of rotation in accord with and upon initiation of rotation of said mass by said angular displacement output of said linkage means; and

F. clutch means providing said discontinuous operative communication of (C) between said linkage means and said inertial mass means and, in addition being further adapted to reestablish said operative communication timed to loom operations and subsequent to presentation of a new warp shed, said reestablished communication thereby causing rapid substantially linear displacement of said shuttle target from said rear position to said forward position, picking the shuttle previously boxed therein and bringing said rotating inertial mass to a halt.

8. The shuttle boxing and picking apparatus of claim 7 wherein said linkage means of (B) comprises two isosceles linkages in back to back relationship.

slip speed of said prime mover prior to said reestablishment of said operative communication by said clutch means. 

1. A cyclic shuttle boxing method for textile loom operations wherein each boxing cycle comprises: a. bringing a shuttle to be boxed into substantially frictionless contact with a shuttle target adapted for substantially linear displacement from a forward position in a shuttle box to a rear position; b. converting the resulting rearward, substantially linear, displacement of said shuttle target into an angular displacement at a location removed from the shuttle box; c. communicating said angular displacement to a rotatable inertial mass at rest, thereby accelerating rotation of said inertial mass while decelerating said shuttle to a complete halt; and d. prioR to the next boxing cycle, i. removing said shuttle from the shuttle box; ii. halting rotation of said inertial mass and iii. returning said shuttle target to its forward position.
 2. The method of claim 1 wherein, subsequent to boxing of said shuttle, picking thereof is achieved, timed to loom operations, by reestablishing communication of said rotating inertial mass with said shuttle target, thus transferring at least a portion of the kinetic energy of said rotating inertial mass to said shuttle target by, seriatim, converting rotational motion of said rotating inertial mass to an angular displacement and converting said angular displacement to a substantially linear forwardly directed displacement of said shuttle target to said forward position thereof, thereby picking said shuttle out of said shuttle box and effectuating steps (d) (i) and (d) (iii).
 3. The method of claim 2 wherein step (d) (ii) is achieved as said shuttle target attains said forward position.
 4. The method of claim 2 wherein acceleration of said rotation of said inertial mass is augmented prior to said reestablishment of communication of said rotating inertial mass with said shuttle target.
 5. The method of claim 4 wherein said augmentation of acceleration of rotation of said inertial mass is achieved by communication thereof with an electric prime mover and acceleration to the slip-speed of said prime mover is attained prior to said reestablishment of communication of said rotating inertial mass with said shuttle target.
 6. Shuttle boxing apparatus for textile looms comprising: A. a shuttle box having disposed therein a shuttle target adapted for substantially linear displacement between a forward position and a rear position by a shuttle received thereagainst; B. linkage means adapted for translation of said substantially linear displacement of said shuttle target to an angular displacement output at a location remote from said shuttle box; C. rotational inertial mass means adapted for discontinuous operative communication with the angular displacement output of said linkage means, said operative communication occurring during the period of displacement of said shuttle target from said forward position to said rear position and ceasing upon attainment of said rear position; and D. means to bring said rotatable inertial mass means to a halt and means to return said shuttle target to said forward position prior to each shuttle boxing cycle.
 7. The shuttle boxing apparatus of claim 6 additionally comprising: E. prime mover means in driving relationship with said inertial mass means, said prime mover means being adapted to drive said rotatable inertial mass means only upon rotation thereof and in either direction of rotation in accord with and upon initiation of rotation of said mass by said angular displacement output of said linkage means; and F. clutch means providing said discontinuous operative communication of (C) between said linkage means and said inertial mass means and, in addition being further adapted to reestablish said operative communication timed to loom operations and subsequent to presentation of a new warp shed, said reestablished communication thereby causing rapid substantially linear displacement of said shuttle target from said rear position to said forward position, picking the shuttle previously boxed therein and bringing said rotating inertial mass to a halt.
 8. The shuttle boxing and picking apparatus of claim 7 wherein said linkage means of (B) comprises two Isosceles'''' linkages in back to back relationship.
 9. The shuttle boxing and picking apparatus of claim 7 wherein said prime mover means comprises a single phase motor.
 10. The shuttle boxing and picking apparatus of claim 9 wherein said inertial mass is accelerated to the slip speed of said prime mover prior to said reestablishment of said operative communication by said clutch means. 